JP2635386B2 - clutch - Google Patents

Description

Description: BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a clutch for switching between two inputs having different rotation directions and different rotation torques and transmitting the input to a driven shaft.

[Conventional technology]

Generally, a continuously variable transmission that transmits rotation of a drive shaft to a driven shaft via a belt-type continuously variable transmission is used for driving wheels such as a scooter.

By the way, since the belt-type continuously variable transmission transmits torque by friction, slippage occurs between the pulley and the belt at the start of operation, a large torque transmission loss occurs, and the driven gear rotated by the belt-type continuously variable transmission is driven. There is a problem that the rising performance until the shaft reaches the high-speed rotation range is poor.

[Problems to be solved by the invention]

Therefore, in addition to the belt-type continuously variable transmission, a second torque transmission device such as a gear transmission device, a chain sprocket transmission device, or a toothed pulley or a toothed belt that does not slip is provided, and the driven shaft is moved by the torque transmission device. When the driven shaft reaches a predetermined number of rotations, the driven shaft is rotated by the belt-type continuously variable transmission.
The rising performance of the driven shaft can be improved.

In this case, a clutch is incorporated between a torque transmission path transmitting torque from the belt-type continuously variable transmission to the driven shaft and a torque transmission path transmitting torque from the second torque transmission device to the driven shaft. It is necessary to switch the transmission path of the rotational torque to the driven shaft.

By the way, in the conventional clutch, since it is configured to be operated by external control, a control device is required.

Therefore, the present invention is to externally control two inputs having different magnitudes or two inputs having different rotation directions output from a second torque transmission device such as a belt-type continuously variable transmission or a gear transmission device. It is an object of the present invention to provide a clutch that can be mechanically switched and transmitted to a driven shaft without any change.

[Means for solving the problem]

In order to solve the above problems, in the present invention,
Externally, the input shaft arranged on the axis of the external theory, and the output shaft arranged coaxially with the input shaft are respectively supported so as to be relatively rotatable, and the inner diameter surface and the output of the external theory are supported. The outer diameter surface of the shaft is a cylindrical surface, and the outer diameter surface and the inner diameter surface of a plurality of sprags incorporated between the two cylindrical surfaces are engaged with the two cylindrical surfaces when the sprags are inclined in the circumferential direction of the outer ring. The retainer provided on the input shaft has pockets into which the outer diameter ends of the sprags enter, and the retainer is provided on the output shaft and fits inside the outer race-side retainer. In the container, a pocket is formed in which the inner diameter end portion of each sprag enters, and in the pocket of the input shaft holder, the outer diameter portions on both sides of each sprag are pressed against each other so that the sprag does not engage with both cylindrical surfaces. Incorporate a pair of elastic bodies to maintain a neutral state, the input shaft and the output shaft With the rotational direction gap is of employing the configuration engaged.

[Action]

With the configuration described above, the input shaft side retainer presses the sprag by rotating the input shaft relative to the output shaft in the right or left direction. The sprag tilts, the arc surface of the sprag engages the cylindrical surface of the outer race and the cylindrical surface of the output shaft, and the clutch operates. When the rotating torque is transmitted to the outer wheel during the operation of the clutch, the rotation of the outer wheel is transmitted to the output shaft via the sprag.

Further, when the input shaft is rotated in the same direction as the outer ring and at a speed higher than the rotation of the outer ring, the input shaft side retainer rotates with respect to the outer ring. At this time, the sprag is caused to be in a neutral state by the contact with the outer ring and the sprag is pushed by the input shaft side retainer, so that the sprag slides on the cylindrical surface of the outer ring.

On the other hand, since the input shaft rotates with respect to the output shaft until there is no clearance in the rotation direction, the rotation of the input shaft is transmitted to the output shaft.

Therefore, for example, if the rotation torque of the belt-type continuously variable transmission is transmitted to the input shaft, and the rotation torque of the second torque transmission device having no slip such as the gear transmission device is transmitted to the outer ring, the belt-type continuously variable transmission is transmitted. The two inputs of the step transmission and the second torque transmission can be mechanically switched and transmitted to the output shaft.

〔Example〕

Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings.

1 to 6 show a first embodiment of the clutch according to the present invention.
The following shows an example. As shown in FIGS. 1 and 2, the inner peripheral surface of the outer race 11 is a cylindrical surface 12. An input shaft 13 is arranged on the axis of the outer ring 11, and the input shaft 13 is rotatably supported by a bearing 14 attached to one end of the outer ring 11. An output shaft 15 is arranged coaxially with the input shaft 13,
The output shaft 15 is rotatably supported by a bearing 16 attached to the other end of the outer ring 11.

The outer diameter surface of the output shaft 15 is a cylindrical surface 17, and a plurality of sprags 18 are incorporated at equal intervals in the circumferential direction between the cylindrical surface 17 and the cylindrical surface 12 of the outer ring 11.

As shown in FIG. 4, the outer diameter surface and the inner diameter surface of the sprag 18 are arc surfaces 19 and 20, and the radius r of each arc surface 19 and 20 is
The distance between the outer ring side cylindrical surface 12 and the output shaft side cylindrical surface 17 is larger than 1/2. The length l in the direction connecting the centers of the arc surfaces 19 and 20 is slightly smaller than the interval δ.
For this reason, in the neutral state in which the sprags 18 stand between the opposed cylindrical surfaces 12, 17, the arc surfaces 19,
A radial armature 21 is formed between 20 and the cylindrical surfaces 12 and 17. Further, when the cylindrical surface 12, 17 is tilted from the neutral state in the circumferential direction, the outer-side circular surface 19 and the inner-side circular surface 20 are engaged with the opposite cylindrical surfaces 12, 17.

The outer diameter end of the sprag 18 fits into a pocket 23 of a retainer 22 provided at the end of the input shaft 13, and the inner diameter end of the sprag 18 is fixed to the end of the output shaft 15. The retainer 24 is stuck in the pocket 25 of the retainer 24.

The dimension A between the circumferential sides of the pockets 23 in the input shaft side cage 22 in the circumferential direction is larger than the dimension B of the circumferential sides of the pockets 25 in the output shaft side cage 24 in the circumferential direction. Further, a concave portion 26 is formed at the center of the side surface of the input shaft side retainer 22 that faces the pocket 23 in the circumferential direction,
A pair of elastic bodies 27 incorporated in the concave portion 26 press the outer diameter side end of the sprag 18 from both sides, and hold the sprag 18 in a neutral state.

Here, as the elastic body 27, a leaf spring, a coil spring, or the like can be used. In the case of this embodiment, an H-shaped notch is formed in the metal ring attached to the inner diameter surface of the input shaft side retainer 22, and the inner portion of the notch is raised to the outer diameter side to make the V-shaped notch.
A letter-shaped elastic piece is provided.

As shown in FIGS. 1 and 3, a square hole 28 is formed in an end face of the input shaft 13 facing the output shaft 15.
At the end face of the output shaft 15, there is provided a square shaft 29 that fits into the square hole 28, and there is a rotational clearance C between the square hole 28 and the square shaft 29.
Are formed.

The clutch shown in the first embodiment has the above structure, and FIG. 7 shows a state in which the clutch is incorporated in a rotational torque transmission system of a scooter in which the wheels 41 are rotated by the operation of the engine 40.

In the above-described device, the toothed pulley 44 and the V pulley 45 are attached to the output shaft 42 of the engine 40 via the centrifugal clutch 43, and the rotation of the toothed pulley 44 is rotated via the toothed belt 46 to form the outer ring of the clutch according to the present invention. 11, and the rotation of the V pulley 45 is transmitted to the input shaft 13 via the V belt 47, and further transmitted to the output shaft 15 of the clutch to the axle 48 of the wheels 41.

For this purpose, the outer ring 11 is provided with a toothed pulley 49, and the input shaft
A V-pulley 50 is attached to 13.

In the above device, V pulleys 45, 50 and V
The input shaft 13 rotated by the belt 47 is
The outer ring 11 is rotated faster than the outer ring 11 rotated via the gears 4 and 49 and the toothed belt 46.

When the clutch is installed as described above, the engine 40
Is driven to rotate the output shaft 42, the rotation of the output shaft 42 is transmitted to the outer ring 11 and the input shaft 13. Its input axis
With the rotation of 13, the input shaft-side cage 22 becomes the output shaft-side cage.
The input shaft side cage 22
As a result, the sprag 18 is pushed, and the sprag 18 falls in the rotation direction of the input shaft side holder 22. For this reason, as shown in FIG. 6, the outer diameter side arc surface 19 and the inner diameter side arc surface of the sprag 18 are formed.
20 is engaged with the opposed cylindrical surfaces 12, 17, and the clutch operates.

On the other hand, the V-belt 47 that transmits the rotational torque from the output shaft 42 to the input shaft 13 has slippage between the V-pulleys 45 and 50 at the initial stage of rotation, and the V-belt 47 transmits the rotational torque from the output shaft 42 to the outer ring 11. Since the transmitting toothed belt 46 reliably transmits the rotation of the output shaft 42 to the outer ring 11, when the engine 40 starts up at a low speed, the rotation of the outer ring 11 becomes the same rotation because the rotation transmitted to the input shaft 13 is a belt slip. .

At this time, the outer ring 11
Is transmitted to the output shaft 15 via the sprags 18 and the wheels
41 rotates.

When the transmission efficiency of the V-belt 47 is improved and the rotation speed of the input shaft 13 is higher than the rotation speed of the outer ring 11, the input shaft side retainer 22 rotates ahead of the outer ring 11, and the outer ring 11 is rotated by the advance rotation. Then, the sprags 18 are caused to come into contact with the arcuate surface 19 on the outer diameter side of the sprags 18 so that the sprags 18 are caused to be in a neutral state. For this reason, the sprag 18 slides on the cylindrical surface 12 of the outer ring 11 and rotates in the same direction as the input shaft side retainer 22, and the outer ring 11
The rotation from 11 is cut off. On the other hand, since the input shaft 13 rotates until the clearance C in the rotation direction disappears and engages with the output shaft 15, the rotation of the input shaft 13 is transmitted to the output shaft 15 by the engagement between the square hole 28 and the square shaft 29. You.

Note that the engine brake during deceleration cannot be used due to slippage between the pulleys 45 and 50 when transmitted by the V-belt 47, but the engine brake can be used from the output shaft 15 through the outer wheel 11.

8 and 9 show a second embodiment of the clutch according to the present invention. In this embodiment, the output shaft 15 '
Is formed in a cylindrical shape, and the input shaft 13 'is inserted inside the output shaft 15'. Then, the square hole 28 and the square shaft 29 shown in the first embodiment are formed.
Instead, an axial ridge 32 is provided on the outer peripheral surface of the input shaft 13 ′, while an axial groove 33 in which the ridge 32 fits is formed on the inner diameter surface of the output shaft 15, and both sides of the groove 33 are formed. A clearance C in the rotation direction is provided between the surface and both side surfaces of the ridge 32.

The other configuration and operation are the same as those of the first embodiment, and thus the description is omitted.

10 and 11 show a third embodiment of the clutch according to the present invention. In this embodiment, the input shaft 13 ″
Are formed as a cylindrical strip, and an output shaft 15 ″ is inserted inside the input shaft 13 ″. Then, instead of the square hole 28 and the square shaft 29 shown in the first embodiment, an axial ridge 34 is provided on the outer peripheral surface of the output shaft 15 ″,
A groove 35 is formed in the inner peripheral surface of the input shaft 13 ″ in which the ridge 34 is fitted. A clearance C in the rotational direction is provided between both side surfaces of the groove 35 and both side surfaces of the ridge 34.

The other configuration and operation are the same as those of the first embodiment, and thus the description is omitted.

In the third embodiment, the gear 36 is formed at the end of the input shaft 13 ", and the rotational torque is transmitted to the gear 36. However, a pulley may be attached.

〔The invention's effect〕

According to the present invention, the clutch is configured as described above, so that a clutch that mechanically switches two inputs transmitted to the input shaft and the outer ring and transmits the input to the output shaft can be realized.

Further, the sprags that fall due to the relative rotation of the input shaft side cage and the output shaft side cage have an outer ring side cylindrical surface and an output side cylindrical surface even when the input shaft side cage rotates in either the right or left direction. , It is possible to incorporate a plurality of the sprags in the circumferential direction between the two cylindrical surfaces, thereby increasing the capacity of the clutch.

Furthermore, since the inner peripheral surface of the outer ring and the outer peripheral surface of the output shaft can be cylindrical surfaces, processing is easy and manufacturing costs can be reduced.

[Brief description of the drawings]

1 is a longitudinal sectional view showing a first embodiment of a clutch according to the present invention, FIG. 2 is a sectional view taken along line II-II of FIG. 1, and FIG. 3 is an input shaft and an output of the same. FIG. 4 is a cross-sectional view showing an assembled portion of the above-described sprags in an enlarged scale, FIG. 5 is a plan view of FIG. 4, and FIG. 6 is an operation state of FIG. FIG. 7 is a schematic view showing an example of the use of the same clutch, FIG. 8 is a longitudinal sectional front view showing a second embodiment of the clutch according to the present invention, and FIG. 9 is IX in FIG. −
FIG. 10 is a cross-sectional view taken along the line IX, FIG. 10 is a longitudinal sectional front view showing a third embodiment of the clutch according to the present invention, and FIG.
It is sectional drawing which followed the -XI line. 11 ... outer ring, 12 ... cylindrical surface, 13, 13 ', 13 "... input shaft, 15, 15'15" ... output shaft, 17 ... cylindrical surface, 18 ... sprag, 19, 20 ... Circular arc surface, 22 cage, 23 pocket, 24 cage, 25 pocket, 27 elastic body, 28, 28 'square hole, 29, 29' square axis, C …… the clearance in the rotation direction,

Claims (1)

(57) [Claims] An outer ring, an input shaft disposed on a shaft center of the outer ring, and an output shaft disposed coaxially with the input shaft are rotatably supported, respectively, so as to be relatively rotatable. The outer diameter surface of the output shaft is a cylindrical surface, and the outer diameter surface and the inner diameter surface of the plurality of sprags incorporated between the two cylindrical surfaces are respectively engaged with the two cylindrical surfaces when the sprags are inclined in the circumferential direction of the outer ring. The retainer provided on the input shaft forms a pocket into which the outer diameter side end of each sprag enters, and is provided on the output shaft and fits inside the outer race retainer. The retainer is formed with a pocket into which the inner diameter side end of each sprag enters, and in the pocket of the input shaft side retainer, the outer diameter portions on both sides of each of the above sprags are pressed against each other to engage the sprag with both cylindrical surfaces. Incorporate a pair of elastic bodies that maintain a neutral Clutch engaged a shaft and an output shaft with a rotational direction gap.